EP2857720A1 - Segment racleur d'huile combiné - Google Patents

Segment racleur d'huile combiné Download PDF

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Publication number
EP2857720A1
EP2857720A1 EP13797980.3A EP13797980A EP2857720A1 EP 2857720 A1 EP2857720 A1 EP 2857720A1 EP 13797980 A EP13797980 A EP 13797980A EP 2857720 A1 EP2857720 A1 EP 2857720A1
Authority
EP
European Patent Office
Prior art keywords
portions
control ring
oil control
spacer expander
oil
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13797980.3A
Other languages
German (de)
English (en)
Other versions
EP2857720A4 (fr
EP2857720B1 (fr
Inventor
Yoshihito Ooya
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Riken Corp
Original Assignee
Riken Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Riken Corp filed Critical Riken Corp
Publication of EP2857720A1 publication Critical patent/EP2857720A1/fr
Publication of EP2857720A4 publication Critical patent/EP2857720A4/fr
Application granted granted Critical
Publication of EP2857720B1 publication Critical patent/EP2857720B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F16J9/066—Spring expander from sheet metal
    • F16J9/068—Spring expander from sheet metal corrugated in the axial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F16J9/066—Spring expander from sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F16J9/203—Oil-scraping rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details

Definitions

  • the present invention relates to a combined oil control ring mounted to a piston for an internal combustion engine, particularly to a combined oil control ring comprising two upper and lower side rails, and an axially corrugated spacer expander having upper and lower portions.
  • oil sludge In automobile engines, a lubricating oil is heated and exposed to a blowby gas during a long period of operation, so that the lubricating oil is contaminated with unburned hydrocarbons and degenerated oil additives (called "oil sludge” as a whole).
  • the oil sludge includes oil sludge precursors having relatively high viscosity.
  • the oil sludge attached to and accumulated on engine parts likely wears the parts and clogs lubricating oil paths, causing troubles in the functions of engine parts such as combined oil control rings (called “oil rings” unless otherwise mentioned).
  • oil rings In the oil rings, spacer expanders and side rails are stuck to each other in the worst case, hindering the movement of separate side rails, and thus failing to exhibit a sufficient oil-controlling function.
  • a conventional combined oil ring 101 comprises a pair of annular side rails 120a, 120b arranged with a gap, and a spacer expander 101 supporting the side rails 120a, 120b.
  • the spacer expander 101 in an axially corrugated form has upper portions 102, lower portions 103, and leg portions 104 connecting the upper portions 102 and the lower portions 103.
  • each space 108a, 108b is defined by each tab 105a, 105b, each projection 106a, 106b, each intermediate portion 107a, 107b, and each side rail 120a, 120b.
  • the side rails 120a, 102b are pressed by radial and axial components of a force due to the inclination angle of the tabs 105a, 105b of the spacer expander 101, thereby exhibiting a function of sealing a cylinder wall and side surfaces of ring grooves of a piston.
  • a small-width oil ring having a small axial width h1 has good followability to a cylinder sidewall with a side-sealing function, resulting in reduced friction loss without increasing oil consumption even if it is a low-tension type.
  • oil sludge is easily accumulated in a space 108a, 108b between the spacer expander and the side rails as described above.
  • the side rails 120a, 120b are highly likely stuck to the spacer expander 101 by the accumulated oil sludge.
  • the accumulation of oil sludge extremely reduces the followability of side rails 120a, 120b to a cylinder wall, resulting in drastically increased oil consumption.
  • JP 2002-310299 A and JP 2003-254155 A disclose a fluororesin coating and a fluororesin-containing resin coating
  • JP 2000-027995 A discloses a coating containing fluoroalkyl-substituted alkoxide
  • JP 2006-258110 A discloses a hydrophilic prepolymer coating containing inorganic polysilazane
  • WO 2011/043364 A1 discloses a method for forming a metal coating having low surface free energy and hydrogen bonding force.
  • These coatings are water-repellant, oil-repellant, or oppositely hydrophilic coatings, or those formed based on methods of preventing the attachment of oil sludge.
  • JUM 59-127856 A discloses an oil ring comprising a spacer expander having upper and lower portions, sufficiently large holes permitting foreign materials such as lead compounds to pass being formed in intermediate portions of the upper and lower portions, such that they do not reach uprising portions of corrugation.
  • USP 5195758 and JP 2011-185383 A disclose spacer expanders having structures preventing the accumulation of oil sludge, which comprise radial grooves in intermediate portions, and oil-exiting holes communicating with the grooves in tabs.
  • JP 2002-310299 A , JP 2003-254155 A , JP 2000-027995 A , JP 2006-258110 A , and WO 2011/043364 A1 suffer excess steps leading to cost increase, and the hole-forming method of JUM 59-127856 A need difficult working, making the oil rings expensive.
  • oil resides in the grooves formed in intermediate portions in US Patent 5195758 and JP 2011-185383 A during the stop of engines, likely suffering the accumulation of oil sludge. As a result, sufficient durability is not obtained in such an operation pattern as undergoing repeated stop of engines.
  • an object of the present invention is provide a combined oil control ring for automobile engines capable of keeping an excellent oil-controlling function without suffering sticking between a spacer expander and side rails for a long period of operation.
  • the combined oil control ring of the present invention comprises two upper and lower side rails, and an axially corrugated spacer expander having upper and lower portions; a leg portion connecting each upper portion and each lower portion of the spacer expander having a portion with an inclination angle ⁇ of 15° or more from the axial direction.
  • the inclination angle ⁇ is preferably in a range of 25° or more.
  • Each of the upper and lower portions is preferably constituted by a tab pressing an inner peripheral surface of the side rail, a projection supporting the side rail, and an intermediate portion between the tab and the projection; at least the intermediate portion comprising a substantially flat pad portion; and a ratio L/P of the circumferential length L of the flat pad portion to a corrugation pitch P being 40% or less.
  • the ratio L/P is more preferably 30% or less, further preferably 20% or less.
  • Each of the upper and lower portions is preferably constituted by a tab pressing an inner peripheral surface of the side rail, a projection supporting the side rail, and an intermediate portion between the tab and the projection; at least the intermediate portion being curvedly projecting toward the opposing side rails.
  • the radius of curvature R of the projection is more preferably in a range of 0.3-3 mm, further preferably in a range of 0.5-1.5 mm.
  • the intermediate portion is preferably inclined such that it becomes more distant from the opposing side rail as it nears the tab.
  • the spacer expander 11 shown in Fig. 1 comprises leg portions 14 having an inclination angle ⁇ of 15° or more to the axial direction, which is larger than in conventional spacer expanders. Accordingly, the spacer expander 11 comprises intermediate flat pad portions 16a, 16b with a relatively short circumferential length L, between upper portions 12 and lower portions 13.
  • curved intermediate portions 26a, 26b projecting toward opposing side rails with a curvature of 1/R may be used as shown in Fig. 2 .
  • the circumferential length L of the flat pad portions 16a, 16b has a close relation to the inclination angle ⁇ of the leg portions 14 of the spacer expander.
  • a larger inclination angle ⁇ tends to reduce the circumferential length L of the flat pad portions 16a, 16b.
  • the inclination angle is preferably in a range of 25° or more.
  • a ratio of the circumferential length L of the flat pad portions to the corrugation pitch P of the spacer expander is preferably 40% or less, more preferably 30% or less, further preferably 20% or less.
  • their radius of curvature R is preferably 0.3-3 mm, more preferably 0.5-1.5 mm.
  • the spacer expander is inclined, such that the intermediate portions become more distant from the opposing side rails as they near the tabs.
  • the spacer expander may be inclined oppositely, such that the intermediate portions become more distant from the side rails as they near the projections. With this inclination, the residence of oil sludge is further prevented.
  • An spacer expander of SUS304 having a nominal diameter d1 of 71 mm, a combined nominal width h1 of 1.5 mm, and a combined thickness a1 of 1.9 mm, and a side rail of SUS440 having a width of 0.4 mm were formed for a combined oil ring.
  • Combined oil control rings of each of Examples 1-3 were attached to first to third cylinders of a 1-liter, 3-cylinder engine. The operation of this engine under the conditions of a predetermined pattern was repeated as an actual engine test. After 250 hours, a side rail gap and the amount of oil sludge attached were measured by the following evaluation methods. Further, an actual engine test was conducted on cylinders having combined oil control rings of each of Examples 4-5 and Comparative Example 1 under the same operation conditions as in Examples 1-3. Each test was conducted three times in each Example and Comparative Example. Top rings and second rings used had the following specifications.
  • each combined oil control ring was removed from the piston, and cleaned with acetone. Thereafter, it was dried at 120°C for 1 hour in an electric furnace, cooled to room temperature in a desiccator, and then measured with respect to its mass to determine its difference from the mass of the combined oil control ring measured in advance before the actual engine test. Differences determined in three actual engine tests were averaged to obtain the amount of oil sludge attached.
  • Examples 1-5 had as large gaps as about 1.5-1.7 times and the amounts of attached oil sludge reduced to 32-80% after the actual engine test, as compared with those of Comparative Example 1. It is considered that in Comparative Example 1 in which the leg portions of a spacer expander had an inclination angle of 10°, the accumulation of oil sludge constrained the side rails, so that the gaps were not returned to the original one (did not expand) even after the pistons were withdrawn from the cylinders, while in Examples 1-5, the attachment and accumulation of oil sludge were reduced, resulting in reduced constraint of the oil rings, and thus expanding the gaps more closely to those before the operation than in Comparative Example 1. It was observed in Example 3 that when the leg portions of the spacer expander had an inclination angle of 25° or more, an extremely smaller amount of oil sludge was attached.
  • Combined oil control rings were produced in the same manner as in Example 1, except that intermediate portions of each spacer expander had curved shapes having a radius of curvature of 1 mm and projecting toward opposing side rails in place of the flat pad portions, and mounted to each cylinder of a 3-cylinder engine to carry out the same actual engine test as in Example 1.
  • the measurement results of all cylinders were averaged. As compared with Comparative Example 1, the gap was 1.6 times, and the amount of attached oil sludge was 32%.
  • Combined oil control rings were produced in the same manner as in Example 1, except that each spacer expander was formed to have leg portions with an inclination angle of 18° only in portions near the upper and lower portions and 50° in middle portions between the upper and lower portions, with intermediate flat pad portions having a circumferential length of 0.5 mm, and mounted to each cylinder of a 3-cylinder engine to carry out the same actual engine test as in Example 1.
  • the measurement results of all cylinders were averaged. As compared with Comparative Example 1, the gap was 1.7 times, and the amount of attached oil sludge was 35%.
  • Combined oil control rings were produced in the same manner as in Example 1, except that each spacer expander was formed to have not only leg portions with an inclination angle of 18° only in portions near the upper and lower portions and 50° in middle portions between the upper and lower portions, but also curved shapes having the radius of curvature shown in Table 3 and projecting toward opposing side rails in place of the intermediate flat pad portions, and mounted to each cylinder of a 3-cylinder engine to carry out the same actual engine test as in Example 1. The measurement results of the actual engine test conducted 3 times were averaged, and are shown in Table 3. Table 3 No.
  • Examples 8-10 were excellent in both of the side rail gap and the amount of attached oil sludge. This reveals that extremely high dischargeability of oil sludge is achieved by the leg portions having as large an inclination angle ⁇ as 50° in middle portions between the upper and lower portions, and as small an inclination angle as 18° only in portions near the upper and lower portions, as well as a drastically increased inclination angle from the intermediate portions, the intermediate projections having a small radius of curvature R.
  • Combined oil control rings were produced in the same manner as in Example 2 (inclination angle ⁇ : 20°, circumferential length L of flat pad portions: 1.2 mm, and L/P: 44%), except that each spacer expander was formed to have intermediate portions inclined by 3° such that they became more distant from opposing side rails as they neared the tabs, and mounted to each cylinder of a 3-cylinder engine to carry out the same actual engine test as in Example 2.
  • the measurement results of all cylinders were averaged. As compared with Comparative Example 1, the gap was 1.61 times, and the amount of attached oil sludge was 33%, which were much improved than in Example 2.
  • oil sludge is less accumulated in a space between the intermediate portions of the spacer expander and side rails, thereby preventing the side rails from sticking to the spacer expander.
  • the intermediate portions are curvedly projecting toward opposing side rails, oil sludge easily flows in both circumferential directions of the intermediate portions. Also, when the intermediate portions are inclined such that they become more distant from the side rails as they near the tabs, oil sludge easily flows inward.
  • the spacer expander constituting the combined oil control ring of the present invention can be formed by usual gears without needing additional steps such as coating and drilling. Because of such structure, of course, oil does not reside in a space between the spacer expander and the side rails while the engine is not operated, resulting in sufficient durability even in an operation pattern having repeated stops of the engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Lubricants (AREA)
EP13797980.3A 2012-05-28 2013-05-27 Segment racleur d'huile combiné Not-in-force EP2857720B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012120628A JP5970239B2 (ja) 2012-05-28 2012-05-28 組合せオイルコントロールリング
PCT/JP2013/064653 WO2013180065A1 (fr) 2012-05-28 2013-05-27 Segment racleur d'huile combiné

Publications (3)

Publication Number Publication Date
EP2857720A1 true EP2857720A1 (fr) 2015-04-08
EP2857720A4 EP2857720A4 (fr) 2016-02-24
EP2857720B1 EP2857720B1 (fr) 2018-04-11

Family

ID=49673259

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13797980.3A Not-in-force EP2857720B1 (fr) 2012-05-28 2013-05-27 Segment racleur d'huile combiné

Country Status (5)

Country Link
US (1) US9657838B2 (fr)
EP (1) EP2857720B1 (fr)
JP (1) JP5970239B2 (fr)
CN (1) CN104334937B (fr)
WO (1) WO2013180065A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2886912B1 (fr) * 2013-12-18 2016-11-23 Kabushiki Kaisha Riken Segment racleur combiné
EP3282148A4 (fr) * 2015-04-09 2018-12-05 Kabushiki Kaisha Riken Segment racleur combiné
EP3282149A4 (fr) * 2015-04-09 2018-12-05 Kabushiki Kaisha Riken Segment racleur combiné

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014209018A (ja) * 2012-08-30 2014-11-06 日本ピストンリング株式会社 組合せオイルリング
DE102014223989A1 (de) * 2014-11-25 2016-05-25 Federal-Mogul Burscheid Gmbh Zweiteiliger Kolbenring
US10520085B2 (en) * 2015-03-31 2019-12-31 Nippon Piston Ring Co., Ltd. Combined oil ring
DE102017108683A1 (de) * 2017-04-24 2018-10-25 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring-Feder für einen Ölabstreifring und Ölabstreifring
JP2020003038A (ja) * 2018-06-29 2020-01-09 株式会社リケン 組合せオイルコントロールリング

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JP2014209018A (ja) * 2012-08-30 2014-11-06 日本ピストンリング株式会社 組合せオイルリング
JP6239964B2 (ja) * 2013-12-18 2017-11-29 株式会社リケン 組合せオイルコントロールリング
JP6228452B2 (ja) * 2013-12-26 2017-11-08 株式会社リケン 組合せオイルコントロールリング

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2886912B1 (fr) * 2013-12-18 2016-11-23 Kabushiki Kaisha Riken Segment racleur combiné
EP3282148A4 (fr) * 2015-04-09 2018-12-05 Kabushiki Kaisha Riken Segment racleur combiné
EP3282149A4 (fr) * 2015-04-09 2018-12-05 Kabushiki Kaisha Riken Segment racleur combiné

Also Published As

Publication number Publication date
WO2013180065A1 (fr) 2013-12-05
EP2857720A4 (fr) 2016-02-24
US9657838B2 (en) 2017-05-23
JP5970239B2 (ja) 2016-08-17
CN104334937B (zh) 2018-12-28
US20150145218A1 (en) 2015-05-28
JP2013245780A (ja) 2013-12-09
EP2857720B1 (fr) 2018-04-11
CN104334937A (zh) 2015-02-04

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